EP0016527B1 - Schlagpresse - Google Patents

Schlagpresse Download PDF

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Publication number
EP0016527B1
EP0016527B1 EP19800300402 EP80300402A EP0016527B1 EP 0016527 B1 EP0016527 B1 EP 0016527B1 EP 19800300402 EP19800300402 EP 19800300402 EP 80300402 A EP80300402 A EP 80300402A EP 0016527 B1 EP0016527 B1 EP 0016527B1
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EP
European Patent Office
Prior art keywords
sleeve
ram
press according
impact press
locking ring
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP19800300402
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English (en)
French (fr)
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EP0016527A1 (de
Inventor
Lennart Jan Lindell
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Individual
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Individual
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Publication date
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Publication of EP0016527A1 publication Critical patent/EP0016527A1/de
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Publication of EP0016527B1 publication Critical patent/EP0016527B1/de
Expired legal-status Critical Current

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J7/00—Hammers; Forging machines with hammers or die jaws acting by impact
    • B21J7/20—Drives for hammers; Transmission means therefor
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/26—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by cams, eccentrics, or cranks
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T83/00—Cutting
    • Y10T83/869—Means to drive or to guide tool
    • Y10T83/8776—Constantly urged tool or tool support [e.g., spring biased]
    • Y10T83/8782—Stored energy furnishes cutting force
    • Y10T83/8784—With reset

Definitions

  • This invention relates to a machine tool referred to herein as an impact press, in that the workpiece-modifying-energy is imparted to the tooling with a substantial impact.
  • the present invention is directed to an impact press wherein a hollow sleeve is reciprocably driven, there being a ram slidable within the sleeve which is normally retained therein during sleeve reciprocation.
  • means are provided for releasing the retaining means at a predetermined point during the reciprocation of the sleeve towards the tooling, whereby the ram is released to move freely in a guided path until it impacts against the tooling.
  • Continued reciprocation of the sleeve is used to recapture the ram as held by the retaining means. The amount of free travel that the ram has can be reduced selectively for use with lighter gauge materials.
  • an impact press comprising in combination: a frame adapted to support a tooling assembly for modifying a workpiece; a reciprocably driven sleeve slidably guided on said frame for movement towards and away from the tooling assembly; a ram slidable between a retracted position with respect to said sleeve and an extended position of impact with a portion of the tooling assembly; means for releasably retaining said ram in said retracted position; and means for releasing said retaining means at a predetermined point during the reciprocation of said sleeve towards the tooling assembly, characterised in that the ram is slidable in and guided only by the sleeve, that the retaining means are carried on said sleeve and extend therethrough to the ram, and that the releasing means are power driven and carried on said frame.
  • the present invention provides an impact press for use with impact responsive tooling.
  • the invention also provides a structure that can be readily fabricated in larger sizes to enable the provision of impact presses without entailing excessive cost and space requirements.
  • the present invention further provides an impact press that can be used with tooling that has a forming capacity, even though its most common usage would involve metal cutting.
  • the ram is really not in the sleeve and is not guided only by the sleeve.
  • the retaining means is not carried on the sleeve and does not extend through it.
  • the only releasing means is the bump 8 which is carried by the frame, but it is not power driven. It is passive and is merely disposed in the way of the descending sleeve as shown in Fig. 3.
  • the spring is never fully disposed in the sleeve, and when the ram is latched as shown in Fig. 2, full energy has not yet been stored in the spring.
  • the retaining means in combination with the power driven releasing means can be actuated by the power driven releasing means at any point during the power stroke of the sleeve, because when the sleeve and ram are as far away as possible from the tooling, the spring already has its full energy stored therein.
  • useful energy begins to be stored during the power stroke after the ram has engaged the hook or latch 7, and then energy is stored only during that portion of the power stroke which is required for the lower end of the sleeve to get down and engage the bump 8. Once the bump has been engaged as shown in Fig.
  • GB - A - 592 462 and DE - B - 1 122 460 both relate to spring hammer machines, such as an automatic centre punch.
  • the main springs of these devices are as unloaded as they can possibly be in their free state, and, in order to provide any useful energy in such springs, it is necessary for the spring hammer first to be applied against the workpiece, and the internal ram is always automatically released when the upper part of the body has reached a predetermined distance from the workpiece.
  • the sleeve 2 has the retaining means 23 that retains the ram 11. Therefore, unlike the present invention there is no frame to support the tooling assembly and the sleeve is not reciprocably driven and is not guided on the frame. Further there is no power driven releasing means.
  • the retaining means latches the ram to the sleeve so that they reciprocate jointly from the beginning of a power stroke, towards the tooling, until the power driven releasing means frees the ram from the sleeve.
  • the power driven releasing means of the present invention overcomes the biasing force of the springs so that, at impact, no shock force is applied to the balls, thus eliminating a wear factor.
  • FIG. 1 An impact press constructed in accordance with the present invention is illustrated in Fig. 1, and is generally indicated by the numeral 20.
  • the illustrated press includes a frame 21 which supports a selected tooling assembly 22 which includes appropriate structure for modifying a workpiece, such as blanking, cut-off, forming or a combination thereof. If desired,. a straightener 23 may be carried on the frame 21 to straighten any strip or wire which then passes to a feeder 24 and to a workpiece clamp or brake 25.
  • the frame 21 includes a base plate 26 on which the impact press 20 is supported, a cap plate 27 on which the tooling 22 and the other accessories are supported, and a pair of spaced vertical side plates 28, 29, there being a guide block 30 therebetween.
  • a motor 31 is pivotally supported on a rod 32 and has an output pulley 33 connected by a belt 34 to a driven pulley 35 which is drivingly supported on a shaft 36 which corotatably carries a gear 37 which meshes with a gear 38 on a shaft 39 which meshes with a gear 40 which is secured to a crankshaft 41.
  • the gear train is also shown in Fig. 11 from above.
  • the crankshaft 41 is supported by two sets of needle bearings 42, 43, each of which has an inner race that directly engages the shaft 41 and an outer race received in a pair of flanged tubu-. lar bearing supports 44, 45 respectively secured to the frame walls 28, 29.
  • a pair of bearing washers 46, 46 separate the gear 40 from the bearing support 44 and the bearing support 45 from a hub described below.
  • the driven crankshaft 41 has an eccentric 47 which is connected to a connecting rod 48 which is connected by a pin 49 to a sleeve 50 which is slidably and reciprocably guided in the guide block 30 of the frame 21.
  • the connecting rod 48 is provided with appropriate bearings at the eccentric 47 and at the pin 49, and the guide block 30 is likewise provided with appropriate sleeve bearings as shown.
  • the gears 37, 38 and 40 are contained within a sealed gear casing 51 best shown in Figs. 1 and 2.
  • the pulley 35 and gear 37 reduce the effective speed of the motor 31, and the gears 38 and 40 are of the same size, so that their rotation is in synchronization but of opposite direction.
  • the space there-beneath will accommodate structure up to a certain size.
  • the illustrated arrangement is compact and structure is enclosed by a housing 52 which has a removable cover on each of its four sides and a removable cover that encloses the tooling assembly 22.
  • the tooling assembly 22 has a downwardly directed portion 22a which projects into an opening 53 which is in alignment with the sleeve 50.
  • the driving means for the sleeve 50 is placed above the frame plate 27, and there is virtually no limit as to how large the structure might be thereabove. In that instance, the sleeve 50 would be reciprocated downwardly to the tooling assembly rather than upwardly to it as shown in the drawings.
  • the sleeve 50 is axially hollow and in its bore 54, there is disposed a ram 55 which is slidably and rotatably carried therein.
  • the ram 55 has an axially facing shoulder 56 which is engageable with the end of the sleeve 50, and this engagement substantially defines a retracted position of the ram 55 within the sleeve 50.
  • the ram 55 is biased by a helical compression spring 58 which acts between the sleeve 50 and the end of the ram 55.
  • the ram 55 has a peripheral groove 57 which forms a part of retaining means described below.
  • the ram 55 When the retaining means are released, the ram 55 is free to move and responds to its inertia of movement and/or bias and the only structure that will arrest such movement is the portion 22a of the tooling assembly which thus substantially defines the extended position of the ram where impact occurs.
  • the spring 58 can be omitted and the inertia present in the ram 55 due to reciprocation will suffice.
  • other structure for storing energy may be used in place of the spring 58.
  • the spring 58 has an unusual or unexpected advantage. In that it is a coil spring, on compression and extension, there is a tendency for the one end to turn with respect to the other, and this torque is applied to the ram.
  • the ram 55 made one complete revolution in 40 strokes, so there is thus incremental rotation on the order of 9 degrees per stroke. Such rotation of the ram is advantageous because the end surface maintains a uniform profile during use.
  • the sleeve 50 and the ram 55 jointly support retaining means generally indicated at 59.
  • the retaining means includes the peripheral groove 57, a number of radial apertures 60 in the sleeve 50, each containing retainer means 61, a portion of which is moveable into the peripheral groove 57 when the peripheral groove 57 is in registration with such retainer means 61.
  • the retainer means 61 in this embodiment includes pairs of spaced balls, there being other embodiments described below.
  • the retainer means 59 further includes a locking ring 62 which is adapted to control the release of the ram 55.
  • the locking ring 62 has an inner peripheral groove 63 which surrounds the sleeve 50, the locking ring being axially slidable on the sleeve and also being capable of rotating on the sleeve.
  • the locking ring 62 is axially biased so that the groove 63 in the ring 62 is urged axially away from the retainer means 61, the bias in this instance being provided by a set of springs 64 which act between a threaded ring 65 carried on the end of the sleeve 50 and the locking ring 62.
  • the bias provided by the spring 58 against the ram 55 urges the edge of the peripheral groove 57 against the retainer means 61, thus biasing the retainer means radially outwardly, but the retainer means 61 is held axially locked by the locking ring 62.
  • the locking ring 62 is shifted axially to place the inner groove 63 in registration with the retainer means 61, the force from the ram groove 57 moves the retainer means radially outwardly and when the grooves are in registration, the ram is axially released.
  • the magnitude of the eccentric 47 determines the travel of the sleeve 50.
  • the point in the cycle where the retaining means 59 is released determines the amount of travel that the ram 55 will be permitted to have as it approaches the tooling portion 22a.
  • the springs 64 act on the locking ring 62 so that the edge of the groove 63 urges the balls of the retainer means 61 endwise against the shank of the ram 55.
  • the ram 55 causes the balls that engage it to rotate along with the surface of the ram, and one ball causes the next one to rotate.
  • the rotation of the ram 55 about its axis also causes the balls of the retainer means 61 to have movement about a vertical axis, the one transmitted to the next and that one transmitting its movement to the ring 62, thus also imparting a slight angular movement to the ring 62.
  • the force is sufficient so that the springs 64 do not prevent such movement.
  • the advantage of this movement is that not only is there no Brinelling by the balls in the groove 57 but there is no Brinelling in the ring groove 63 either, thus the surfaces of these grooves being kept smooth in spite of repeated and extensive use.
  • the springs 64 are free to expand and thus the ring 62 is moved back to its fully retracted position, preparatory to the next stroke.
  • the sleeve 50 resumes its travel in the opposite direction, and the spring 58 expands slightly to provide a rather slight gap at the ram shoulder 56 as shown in Fig. 5 and in Fig. 3 so that the retainer means 61 acts on the lower edge of the ram groove 57.
  • releasing means refers to structure 66-76 on the frame for releasing the retaining means 59, and such structure is found in several of the views.
  • the releasing means is best shown in Figs. 9 and 10.
  • the crankshaft 41 is provided with a hub 66 keyed thereto and a radially split eccentric 67 is clamped to the hub 41 by means of an appropriate pin and screw arrangement 68.
  • the eccentric 67 functions as such as it carries an eccentrically located screw 69 to which is connected a connecting link 70.
  • a control shaft 71 is secured to and supported by bearings in the frame walls 28, 29, there being at least one release arm 72, 73 extending radially from the control shaft 71. As best seen in Fig.
  • each of the release arms 72, 73 has a roller 74 engageable with the lower end surface of the locking ring 62.
  • the structure for transferring movement from the link 70 to the control shaft 71 is best shown in Fig. 9.
  • the connecting link 70 is connected to a plunger 75 which engages an end of a drive arm 76 which is carried on the control shaft external to the frame wall 29.
  • the drive arm 76 thus rocks the control shaft 71 at a selected time which is picked in relation and thus in response to the axial position of the sleeve 50.
  • a handle 77 and a stop 78 On the other end of the control shaft 71, namely the left end shown in Fig. 12, there is a handle 77 and a stop 78, the handle being secured to the shaft 71.
  • the handle or lever 77 engaging the stop 78 limits the amount that the rollers 74, 74 can move downwardly away from the locking ring 62.
  • the lever or handle 77 can also be utilized .as a manual actuator in connection with setting the desired position of the eccentric 67 of the releasing means.
  • the drive arm 76 includes a pin 79 which is spring loaded and which is slidable therein.
  • a solenoid 80 can be energized to effect retraction of the pin 79.
  • the driving means on the frame also includes driving structure for coordinating the feeder 24 and the workpiece brake 25.
  • the feeder 24 may be of conventional construction and it grips a workpiece, advances it, releases the grip on the workpiece, and then returns to the place from which it came to regrip the workpiece.
  • the workpiece brake is preferably held actuated so that the workpiece cannot move during the time that the feeder 24 is disengaged to move back to regrip the workpiece.
  • the workpiece brake is shown schematically at 25 in Fig. 9 and it has a spring-loaded plunger 81. There is a linkage provided to actuate the brake 25 in coordination with the movement of the ram.
  • the shafts 39 and 41 are driven at the same speed and are synchronized with each other by the gears 38, 40.
  • Carried on a central portion of the shaft 39 is a bellcrank 82 pivoted on a shaft 83.
  • One arm of the bellcrank 82 is in registration with the plunger 81 and the other or lower arm of the bellcrank 82 has a roller that follows the periphery of a cam 84 which is keyed to the shaft 39.
  • An adjusting screw 85 determines the amount 6f travel that will be imparted to the plunger 81 to allow for various thicknesses of workpiece.
  • the feeder 24 is also actuated in synchronization with the movement of the sleeve 50 and is driven by the shaft 39.
  • a reciprocable portion 86 projects through a slot in the frame plate 27 and has a sliding connection with an arm 87 pivotally carried on a shaft 88.
  • the feeder is thus reciprocated horizontally.
  • the shaft 88 projects toward the viewer in Fig. 10 through the wall 29, and on the outer end, the shaft 88 carries a downwardly extending arm 89 pivotally connected at 90 to a further arm 91 which has a pivotal connection 92 with an adjustable cross-slide 93 which is carried on the end of the shaft 39 as best shown in Fig. 11.
  • the tooling assembly 22 may have a feature which also requires coordination with the other parts of the machine. It is so assumed in the present instance, and it is further assumed that appropriate control or regulation can be provided by appropriate rocking of a shaft or regulator 94.
  • a lever 95 is clamped thereto and a connecting rod 96 of adjustable effective length is pivotally connected to the lever 95 and to one end of a further lever 97, the latter being pivoted to the frame at 98.
  • the lever 97 supports a roller 99 which functions as a cam follower in engaging a cam surface 100 which may form the outer periphery of the hub 66.
  • any regulation of the tooling is carried out in synchronization with the movements of the sleeve 50.
  • crankshaft 41 rotating through the belt-and- gear drive rotates the crankshaft 41 to reciprocate the sleeve 50.
  • This same crankshaft also regulates and drives the releasing means which are engageable with the locking ring at a selected point in the cycle of operation to release the locking ring, thereby freeing the ram to impact against the tooling.
  • Continued rotation of the crankshaft removes the force needed to operate the locking ring and continued advancement of the sleeve toward the tooling causes the ram to be recaptured in its retracted position in the sleeve, owing to the reactive force from the tooling.
  • Appropriate linkages driven by the same gearing reciprocate the feeder, actuate the workpiece brake, and regulate the tooling if necessary.
  • FIGs. 13-17 illustrate some further retaining means.
  • Each of these uses a ram 100-104 that has therein a peripheral groove 105-108, the ram 104 having a second peripheral groove 109.
  • These modifications each include a sleeve 110-113 with radial apertures that receive various retainer means therein.
  • Each of these embodiments has a locking ring 114-117 adapted to control the release of the ram, each having an inner peripheral groove 118-121, the locking ring 117 having a second inner peripheral groove 122.
  • the peripheral grooves 108 and 121, and 109 and 122 respectively move into registration at the same time.
  • the retainer means 61 in each instance includes balls, in Figs. 14 and 17 they include pairs of balls, in Fig. 14 they include spacer pins 123 between pairs of balls, and in Fig. 15 there is a locking ring 124 which can exert a very powerful grip on the ram since there is line contact virtually the entire circumference of the ram 103.
  • the impact press is limited in rate of operation to about 180 strokes per minute. Without such a feeder, smaller workpieces can be made or modified at a normal rate of 500 strokes per minute.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Press Drives And Press Lines (AREA)

Claims (22)

1. Schlagpresse, bestehend aus einem Rahmen (26 bis 29) zur Unterstützung einer Werkzeuganordnung (22) für die Bearbeitung eines Werkstücks, einer hin- und hergehend angetriebenen Hülse (50), die gleitend am Rahmen (28, 29) bei der Bewegung in Richtung auf und weg von der Werkzeugan-ordnung (22a) geführt ist, einem Bären (55), der gleitend zwischen einer zurückgezogenen Stellung in Bezug auf die Hülse (50) und einer vorbewegten Schlagstellung mit einem Teil (22a) der Werkzeuganordnung (22) geführt ist, einer Einrichtung (57, 61, 63) zum freigebbaren Halten des Bären (55) ub der zurückgezogenen Stellung und einer Einrichtung (71, 72, 74, ...) zum Auslösen der Halteeinrichtung (59) an einem vorbestimmten Punkt während der Bewegung der Hülse (50) in Richtung auf die Werkzeuganordnung (22), dadurch gekennzeichnet, daß der Bär (55) nur in der Hülse (50) gleitet und geführt ist, daß die Hatte-, einrichtung (59) von der Hülse (50) getragen ist, durch die hindurch (61) sie sich zum Bären (55) erstreckt, und daß die Auslöseeinrichtung (71, 72, 74,...) kraftgetrieben und vom Rahmen (26 bis 29) getragen ist.
2. Schlagpresse nach Anspruch 1, dadurch gekennzeichnet, daß der Rahmen (26 bis 29) eine Einrichtung zum hin- und hergehenden Antreiben (41, 47, 48) der Hülse (50) und zum damit synchronen Betätigen (67, 70) der Auslöseeinrichtung (71, 72, 74, ...) trägt.
3. Schlagpresse nach Anspruch 2, gekennzeichnet durch eine zur Antriebs- und Betätigungseinrichtung gehörende angebreibene Kurbelwelle (41), die vom Rahmen (28, 29) unterstützt ist, ein Pleuel (48), das zwischen einem Exzenter (47) auf der Kurbelwelle (41) und der Hülse (50) wirksam ist, und ein Verbindungsglied (70), das zwischen einem weiteren Exzenter (67) auf der Kurbelwelle (41) und der Auslöseeinrichtung (71, 72, 74, ...) wirksam ist.
4. Schlagpresse nach Anspruch 2, dadurch gekennzeichnet, daß die Antriebseinrichtung ein erstes Gliederwerk (86, 87, 88, 89, 91, 93, 39) zum Betätigen einer hin- und herbewegbaren Zuführvorrichtung (24) für das Werkstück in einem einstellbaren Ausmaß aufweist.
5. Schlagpresse nach Anspruch 4, dadurch gekennzeichnet, daß die Antriebseinrichtung ein zweites Gliederwerk (84, 82, 85) zum Betätigen einer Werkstückbremse (25) während des Zurückziehens der Zuführvorrichtung (24) in einem einstellbaren Ausmaß der Betätigung aufweist.
6. Schlagpresse nach Anspruch 5, dadurch gekennzeichnet, daß die Antriebseinrichtung ein weiteres Gliederwerk (94 bis 100) aufweist, das mit der Werkzeuganordnung (22) verbindbar ist.
7. Schlagpresse nach Anspruch 1, gekennzeichnet durch eine Feder (58), die ständig gänzlich in der Hülse (50) angeordnet ist und zwischen der Hülse (50) und dem Bären wirkt und in der die volle Energie gespeichert ist, wenn sich der Bär (55) in der zurückgezogenen Stellung befindet.
8. Schlagpresse nach Anspruch 1, dadurch gekennzeichnet, daß der Bär (55) eine Umfangsschulter (56) aufweist, die in axialen Eingriff mit der Hülse bringbar ist und im wesentlichen die zurückgezogene Stellung während dieses Eingriffs bestimmt.
9. Schlagpresse nach Anspruch 1, gekennzeichnet durch eine Umfangsnut (57) am Bären (55) innerhalb der Hülse (50) als Teil der Halteeinrichtung (59), einen Halter (61) in der Hülse (50), der bei gegenseitiger Ausrichtung mit einem Abschnitt in die Umfangsnut (57) bewegbar ist, und einen auf der Hülse (50) gleitend axial verschiebbaren Verriegelungsring (62) mit einer die Hülse (50) umschließenden Innenumfangsnut, wobei die Umfangsnut (57) des Bären (55) den Halter (61) radial nach außen drückt, jedoch vom Verreigelungsring (62) in axialer Verriegelung gehalten wird, und der Bär (55) von der Hülse (50) axial freigegeben wird, sobald die kraftgetriebene Auslöseeinrichtung (71, 72, 74) die Nuten (57, 63) in Ausrichtung aufeinander bewegt hat.
10. Schlagpresse nach Anspruch 9, gekennzeichnet durch eine zweite Umfangsnut (109) am Bären (104), einen zweiten Halter in der zweiten Nut und eine zweite Innenumfangsnut (122) am Verriegelungsring (117), wobei die Bärnuten (108, 109) gleichzeitig auf die Ringnuten (121, 122) ausrichtbar sind.
11. Schlagpresse nach Anspruch 9, dadurch gekennzeichnet, daß der Halter einen Ring (124), der in die Nut (107) des Bären (103) bewegbar ist, und Kugeln aufweist, die in die Nut (120) des Verriegelungsrings (116) bewegbar sind.
12. Schlagpresse nach Anspruch 9, dadurch gekennzeichnet, daß der Halter Paare von Kugeln aufweist, wobei eine Kugel eines jeden Paares in die Bärennut (106) und die andere Kugel jedes Paares in die Verriegelungsringnut (119) bewegbar ist.
13. Schlagpresse nach Anspruch 12, dadurch gekennzeichnet, daß zwischen den Kugeln eines jeden Paares Abstandsstifte (123) angeordnet sind.
14. Schlagpresse nach Anspruch 9, gekennzeichnet durch eine Feder (64), die zwischen der Hülse (50) und dem Verriegelungsring (62) wirksam ist und eine Vorspannung liefert.
15. Schlagpresse nach Anspruch 7; dadurch gekennzeichnet, 'daß der Bär (55) innerhalb der Hülse (50) drehbar ist und die Feder (58) eine Schraubendruckfeder ist, die dem Bären (55) während seiner Ausfahrbewegung einen Drehzuwachs erteilt.
16. Schlagpresse nach Anspruch 9, gekennzeichnet durch eine Schraubendruckfeder (58), die zwischen der Hülse (50) und dem Bären (55) wirkt, wobei der Bär innerhalb der Hülse (50) und der Verriegelungsring (62) auf der Hülse (50) drehbar sind und die Schraubendruckfeder (58) dem Bären (55) während seiner Ausfahrbewegung einen Drehzuwachs erteilt, wobei der Halter (61) aus Kugeln besteht und die Drehung des Bären (55) mit Reibung über die Kugeln (61) wirkt und auch dem Verriegelungsring (62) einen Drehzuwachs erteilt.
17. Schlagpresse nach Anspruch 2, dadurch gekennzeichnet, daß die Antriebs- und Betätigungseinrichtung eine Antriebswelle (41) aufweist, die drehbar im Rahmen (28, 29) gelagert und zur Hin- und Herbewegung der Hülse (50) verbunden ist und daß mit der Antriebswelle (41) an vorbestimmter Stelle in Bezug auf ihre Drehachse eine Exzenterscheibe (47, 48) verkeilt ist, die einen Teil der Einrichtung zum Betätigen der Auslöseeinrichtung (71, 72, 74, ...) bildet.
18. Schlagpresse nach Anspruch 2, dadurch gekennzeichnet, daß die Halteeinrichtung (59) einen Verriegelungsring (62) aufweist, der gleitend auf der Hülse (50) getragen ist und der Steuerung der Freigabe des Bären (55) dient, und daß die Antriebs- und Betätigungseinrichtung eine hin- und herbewegbar vom Rahmen (28, 29) getragene Steuerwelle (71) aufweist, von der sich wenigstens ein Auslösearm (72, 73) in radialer Richtung erstreckt und mit dem Verriegelungsring (62) in Eingriff bringbar ist, um ihn in axialer Richtung auf der Hülse (50) zu verlagern, wobei ein Antriebsarm (76) zur Hin-und Herbewegung der Welle (71) in Bezug auf die axiale Stellung der Hülse (50) vorgesehen ist.
19. Schlagpresse nach Anspruch 1, gekennzeichnet durch eine Einrichtung (79, 80) zum wahlweisen Unwirksammachen der Auslöseeinrichtung (71, 72, 74, ...).
20. Schlagpresse nach Anspruch 18, gekennzeichnet durch eine Einrichtung (79, 80) zum wirksamen Abkuppeln eines der Arme (72, 73).
21. Schlagpresse nach Anspruch 18, gekennzeichnet durch einen vom Antriebsarm (76) getragenen, solenoidbetätigten Stift (79), der wahlweise zurückziehbar ist, um ein Freigeben des Bären (55) auszuschließen.
22. Schlagpresse nach Anspruch 17, dadurch gekennzeichnet, daß die Auslöseeinrichtung (71, 72, 74, ...) eine vom Rahmen (28, 29) hin- und herbewegbar getragene Steuerwelle (71) aufweist, von der aus sich wenigstens ein Auslösearm (72, 73) radial erstreckt, um mit der Halteeinrichtung (59) zusammenzuwirken, daß ein Antriebsarm (76) zum Hin- und Herbewegen der Steuerwelle (71) in Abhängigkeit von der axialen Stellung der Hülse (50) vorgesehen ist und daß der Antriebsarm (76) vom Exzenterantrieb (47, 48) angetrieben ist.
EP19800300402 1979-02-22 1980-02-12 Schlagpresse Expired EP0016527B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US06/014,093 US4245493A (en) 1979-02-22 1979-02-22 Impact press
US14093 2001-12-10

Publications (2)

Publication Number Publication Date
EP0016527A1 EP0016527A1 (de) 1980-10-01
EP0016527B1 true EP0016527B1 (de) 1982-12-29

Family

ID=21763497

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19800300402 Expired EP0016527B1 (de) 1979-02-22 1980-02-12 Schlagpresse

Country Status (8)

Country Link
US (1) US4245493A (de)
EP (1) EP0016527B1 (de)
JP (1) JPS5921691B2 (de)
CA (1) CA1119848A (de)
CH (1) CH647432A5 (de)
DE (1) DE3061464D1 (de)
NL (1) NL186797C (de)
WO (1) WO1980001766A1 (de)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4309929A (en) * 1980-02-20 1982-01-12 Leesona Corporation Trim press having hammer drive for punch
US4470330A (en) * 1983-02-22 1984-09-11 Lindell Lennart J Tooling assembly for an impact press
US5438225A (en) * 1992-02-06 1995-08-01 Murphy Management Inc. Solar powered annuciator
US5927140A (en) * 1997-12-16 1999-07-27 The Whitaker Corporation Tool accelerator
US6571596B1 (en) * 2000-11-29 2003-06-03 Lennart J. Lindell Automatic two-station adiabatic blank cut-off and part forming system
US7866521B2 (en) * 2004-12-03 2011-01-11 Black & Decker Inc. Magazine for wired-collated fasteners with automatic loading
US7537145B2 (en) 2007-02-01 2009-05-26 Black & Decker Inc. Multistage solenoid fastening device
US20100092328A1 (en) * 2008-10-09 2010-04-15 Glenn Thomas High velocity adiabatic impact powder compaction
CN113458241B (zh) * 2021-05-15 2022-08-26 黑龙江省科学院智能制造研究所 一种用于铝合金型材的冲压设备

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE195625C (de) *
US1006873A (en) * 1909-12-18 1911-10-24 John Harry Phillips Spring-hammer.
US1053744A (en) * 1911-08-22 1913-02-18 John H Phillips Spring-hammer.
US1221421A (en) * 1916-04-17 1917-04-03 Glenn F Crosiar Power-hammer.
US1465918A (en) * 1921-12-06 1923-08-21 Joseph M Redinger Spring hammer
US1747842A (en) * 1927-12-09 1930-02-18 John E Phillips Calking or tamping tool
US2245879A (en) * 1940-01-20 1941-06-17 Theodore T Sossner Monogram engraving machine
GB592462A (en) * 1943-02-26 1947-09-18 Sarl Mermet & Virthner Automatic centre punches, chisels, hammers and like impact tools
US2641941A (en) * 1948-06-16 1953-06-16 Edgar C Lundeberg Actuating mechanism for impact machines
FR1099458A (fr) * 1953-12-18 1955-09-06 Seignol Presse ou potence de frappe à inertie
DE1122460B (de) * 1959-02-13 1962-01-18 Ind Diffusion Murex S A L Admi Federhammer fuer starke Einzelschlaege
IT994366B (it) * 1972-10-07 1975-10-20 Daisuzu Meriyasu Kogyo Kk Apparecchio per il taglio di materiali in foglio a strati sovrapposti
US3854356A (en) * 1973-07-17 1974-12-17 Amf Inc Thread cutting and clamping means
SU561597A1 (ru) * 1974-06-04 1977-06-15 Механизм высадки головок на детал х

Also Published As

Publication number Publication date
NL186797C (nl) 1991-03-01
EP0016527A1 (de) 1980-10-01
WO1980001766A1 (en) 1980-09-04
JPS56500206A (de) 1981-02-26
NL8020045A (nl) 1980-12-31
US4245493A (en) 1981-01-20
CA1119848A (en) 1982-03-16
NL186797B (nl) 1990-10-01
JPS5921691B2 (ja) 1984-05-22
CH647432A5 (de) 1985-01-31
DE3061464D1 (en) 1983-02-03

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